Hydraulic means for controlling the movement of a ring or spindle rail



Oct. 22, 1968 H. TURK ETAL 3,406,919

HYDRAULIC MEANS FOR CONTROLLING THE MOVEMENT OF A RING OR SPINDLE RAIL 2 Sheets-Sheet 1 Filed July 2, 1965 Fl G. l

mveuroas: HERBERT TURK JOANNES SNELS CARSTEN RAMCKE BY Mdpov! AT T'YS Oct. 22, 1968 H. TURK ETAL 3,

HYDRAULIC MEANS FOR CONTROLLING THE MOVEMENT OF A RING OR-SPINDLE RAIL Filed July 2. 1965 2 Sheets-Sheet 2 INVENTORS: HERBERT TURK JOANNES VSN'ELS CARSTEN RAMCKE ATTYS United States Patent 3,406,919 HYDRAULIC MEANS FOR CONTROLLING THE MOVEMENT OF A RING OR SPINDLE RAIL Herbert Turk, Remscheid-Lennep, and Carsten Ramcke, Wuppertal-Ronsdorf, Germany, and Joannes Snels, Rheden, Netherlands, assignors to Barmer Maschinenfabrik AG., Wuppertal-Oberbarmen, Germany Filed July 2, 1965, Ser. No. 469,107 Claims priority, application Germany, July 8, 1964,

6 Claims. of. 242-26.4)

ABSTRACT OF THE DISCLOSURE A process and apparatus for rapidly returning a ring or spindle rail to its lowered starting position in which process an amount of ressure fluid per unit time is conveyed The present invention relates generally to an improved winding process and to apparatus for carrying out said winding process. More particularly, the invention is directed to a process and apparatus for the distribution of thread with a great crossing angle outside of the winding process proper and for rapidly returning the ring or spindle rail of spinning and ring twist machines to their lowcred starting position. Upward'and downward movements of the ring or spindle rail have the same, different, or possibly nonhomogeneous speeds, which movements are produced by a hydraulically driven traverse mechanism having a range of movement extending axially beyond the winding construction.

After the completion of the yarn winding, it is customary in mechanically driven traverse mechanisms to return the ring or spindle rails as rapidly as possible, going beyond the traverse range, downward or upward to their starting position for the commencement of the next winding formation in order to distribute the thread by this operation in a steep spiral for the facilitation of the re-finding of the thread end. The mechanisms and switching devices that are needed for this purpose are well known. Likewise, pneumatic accessory devices for such mechanisms are known by means of which the lowering of the ring rail to its starting position can be accomplished.

Where the spinning or ring twist machines are equipped with hydraulically driven traverse mechanisms, however, such mechanical means require a complicated and spaceconsuming installation. The principal objective of the present invention, therefore, is to develop a simplified process and apparatus so as to make it possible to utilize the existing hydraulic apparatusto provide simultaneously for the automatic and rapid returning of the ring or spindle rail to its lowered starting position.

In order to accomplish the above objective, it is proposed, according to the present invention, that in the returning of the ring or spindle rail toits lowered starting position and/or in the possible stagewise startingof the ring or spindle rail from the starting position up to the position where the transverse motion commences there is conveyed into or out of the hydraulic working cylinder an amount of pressure fluid per unit time which is greater than that utilized during the whole winding process. The apparatus that is used to carry out the process is char- 3,406,919 Patented Oct. 22, 1968 acterized by the feature that in the hydraulic installation (of the hydraulic traverse mechanism) which supplies the energy. needed to shift the working piston, meansare provided to generate a hydraulic reserve energy, which means are engageable for the returning of the ring or spindle rail to its starting position after completion of the winding construction and/or for the movement to the traverse commencement position.

By means of the subject invention, the pump unit of the apparatus has only to be designed for the performance of the magnitude of the traverse movements so that a continuous power loss by conveying excess and unused liquid is largely avoided which otherwise would occur during the entire winding construction if the pump unit were adjusted constantly for the conveyance magnitude of the maximum requirement for the lowering of the ring or spindle rail;

In order with the simplest pOSSible means and'without difficulties to make possible a subsequent installation in hydraulic traverse mechanisms already available and in further development of the invention, it is proposed that in the hydraulic installation, on a branch from the pressure line between the reversal control valve for the direction change of the pressure fluid acting on the working piston on alternating sides and the pressure pump there be provided a pressure storer which, in case of need, supplies the additional amount of pressure fluid. The same, similarly favorable result is obtained by the'use of pumps with variable conveyance amount, or pumps whose drive motor is variable in its rate of revolution in steps or infinitely. Moreover, a rapid lowering of the ring rail can be achieved without an additional pressure supply" source or without time performance heightening of the supply sources on hand, by using the weight of the ring rail itself as additional drive, which is superimposed on the pump energy present. Here a rapid lowering is made possible through the feature that the two chambers of the working cylinder are joined by a short-circuit line in which one or more blocking members are provided, of which at least one is controllable.

The advantage of the jolt-free manner of operation of hydraulic drives is here fully utilized, especially in the catching of the rapidly moving ring rail. Although the ring or spindle rail is here stopped almost without braking path and abruptly there does not occur any undesirable recoiling. The possibly stepless modification of the flowing amount of pressure fluid allows an exact adjust- ,ment of the return speed corresponding to the requireand FIGURE 2 is a schematic representation ofa modified arrangement of the same apparatus. According to FIG. 1, the hydraulical y driven traverse mechanism consists essentially of ring rail 1, which is suspended on draw straps 2, which, in turn, are fastened over deflection rollers 3 continuously with their other ends attached to piston rod 4 of working piston 6 which is acted upon on both sides and conducted in the hydraulic cylinder 5. Switching feeer 7, seated on pistrn rod 4, moves back and forth between end switches 8 and 9 and, through'their actuation, brings about in each case the stroke reversal of the working pTston 6 and thereby the direction reversal both of its own movement and also that of ring rail 1. If need be, there are additionally arranged on threaded spindles 10 and 11 which move end switches 8 and 9 according to program, also control switches 12 and 13, which, for example at the stroke ends, initiate or terminate acceleration sections for the ring rail movement, as is described more fully below.

The hydraulic working circuit belonging to the working cylinder is composed, for example, of pressure pump driven by motor 14, reversing valve 16, two quantity regulators 17 and 18, whose passage cross sectons are permanently set for a certain opening size, and two nonreturn valves 19 and 20 switched parallel to quantity regulators 17 and 18, as well as adjustable choke member 21, both of whose passages likewise lie parallel each to one of the quantity regulators 17 and 18. All the control elements of the hydraulic operating and control circuits are connected with one another over lines (not shown). In the control circuit of choke member 21 there are arranged a control valve 22 and also an adjustable quantity regulator 23 seated in each case in the return of this control circuit. To the pressure line between pump 15 and reversing valve 16 there is connected a branch which connects the hydraulic working circuit with a pressure storer 24. All the return lines of the hydraulic control and operating circuits as well as the leakage oil lines (not represented) end in the common supply tank 25. Pressure regulating devices (not shown) with overflow possibility into the supply tank 25 provide that in the whole hydraulic system a certain maximum pressure is not exceeded. Since the pressure storer 24 is constantly in communication with the hydraulic line system, the stored pressure is always equal to that prevailing the line conduction system, unless the latter falls below a certain minimum value, so that for the protection of the storer a nonreturn valve installed in this closes.

In the traverse movement during the winding formation the switching feeler 7 moves back and forth between end switches 8 and 9, which are alternately operated by the former. End switches 8 and 9 act as stroke limiting switches, by switching the reversal control valve 16 in their actuation over an electric control part (not shown), which valve 16, then, in turn, guides the pressure fluid alternately to the left and then to the right-hand chamber of working cylinder 5, in which process in each instance quantity regulator 17 or 18 situated in the flow of the pressure fluid emerging from the cylinder is determinative for the constant, possibly differing stroke speed of the working piston or of ring rail 1.

If during a traverse stroke, acceleration or retardation sections are intended, these can be initiated, for example, by control switch 12 or 13 and, possibly, terminated by end switches 8 and 9. In this case control switches 12 and 13 as well as end switches 8 and 9 operating as stroke reversal switches act on the control valve 22 over an electric control part. On operation of the first two switches by switching feeler 7 the control valve 22 is brought in each case into that one of the two switching positions in which the pressure fluid drives with choke member 21 at a speed adjusted by the quantity regulator 23 in the sense of a constantly increasing cross-sectional opening, whereby the pressure fluid amount per time unit emerging from the one side of the working cylinder 5 gradually rises and thereby the speed of operating piston 6 and ring rail 1 becomes greater in like measure. Before the maximum passage cross-section of choke member 21 is reached, switching feeler 7 strikes against end switch 8 or 9, by which the control valve 22 is then switched over in such a way that choke member 21, under the influence of the pressure fluid, again slowly closes and, consequently, the speed of working piston 6 and ring rail 1 is retarded.

Depending on the type of winding construction, the traverse stroke is constantly displaced in the course of the winding formation, or shortened or lengthened. In the present case these processes are controlled by shifting end switches 8 and 9 by means of threaded spindles 10 and 11, which, in turn, are driven according to a shifting program over a gear not shown in detail.

Toward the end of the winding process one of the end switches 8 or 9 advanced by threaded spindles 10 and 11 operates a blocking switch (not shown) arranged in its conveyance path which, in turn, initiates the restoration of all of the control and switching members involved, as well as the rapid return of ring rail 1, into their starting position for the commencement of the next winding formation.

In detail, this restoration takes place as follows: After operation of the above mentioned blocking switch by end switch 8, switching feeler 7 moving back and forth strikes against control switch 12, which, as described above, brings about the opening of choke member 21 and thereby the acceleration of ring rail 1. Continuing to run in the original direction, switching feeler 7 reaches and operates end switch 8, whereby reversal control valve 16 is thrown over in such a way that the pressure fluid flow in working cylinder 5 and the directions of movement of working piston 6 and ring rail 1 are reversed. In contrast to the constant closing of choke member 21 on operation of end switch 8 in the course of the preceding winding formation, the closing of the passage cross-section in choke member 21 is now brought about. On the contrary, its passage cross-section remains open, so that its greatest passage cross-section is free and the greatest possible amount of pressure fluid can emerge from working cylinder 5. In the event that during the winding formation no accelerations are provided in the main stroke, control switches 12 and 13, if present at all, do not enter the action. End switch 8 then additionally takes over at the end of the winding formation-as a consequence of its action on the blocking switch-the function of control switch 12, namely, the initiation of the opening of choke member 21 to its maximum passage cross-section. This passage cross-section permits an amount of flow per second which is greater than that for which the hydraulic pump is designed. Thereby, after the opening of the choke member into the other chamber of working cylinder 5, a correspondingly equal amount of liquid flows. As additional fluid source the pressure storer 24 supplies pressure fluid into the line between pressure pump 15 and reversal control valve 16. The ring bank 1 now travels to its starting position for the commencement of the next winding formation at a considerably higher speed than at any point of time during its normal traverse movement.

In another form of execution of the invention the temporary extra requirement in pressure fluid per time unit for the restoration of ring rail 1 to its starting position is achieved with the choke member 21 completely open by increasing the flow of fluid from the pump. This can be accomplished in such a manner that on operation of the blocking switch by one of the end switches 8 or 9 the turning speed of the motor driving the pump is increased, for example, by pole reversal or feed frequency alteration. A further possibility of execution consists in providing a pump adjustable in its conveyance amount, whose shifting takes place on operation of the blocking switch toward the end of the winding formation over suitable drive elements.

In the same manner, that is, by complete opening of choke member 21 and use of additional pressure fluid supply sources, it is possible, after corresponding provisions are made in the program shifting system, for the restarting of the ring or spindle rail from its starting position into the traverse commencement position to be carried out at increased speed, possibly also with time interruptions, for example, by cutting in a short-circuit line between pump pressure line and supply tank 25, as, for example, in order to set up a thread reserve.

In FIG. 2, there is represented a modification of the hydraulic system as compared to FIG. 1. Here an additional pressure storer is not provided, nor are any measures taken to raise the capacity of the pump. Working cylinder 5 has a so-called short-circuit line 26 connecting the two cylinder chambers, which makes it possible to obtain the result that the amount per time unit of pressure fluid flowing into the working cylinder or out of it in the returning of the ring or spindle rail to the starting position is greater than at any arbitrary point of time during the winding process. In the short-circuit line 26 there are seated two oppositely effective nonreturn valves, of which one, designated 27, can be opened by switching of the control valve 28-.

Control valve 28 is connected over the electric control portion (not shown) with the blocking switch (likewise not shown) on the conveyance path of end switches 8 and 9 by electrical lines. On operation of the blocking switch by end switches 8 and 9 toward the end of the winding formation, the control valve 28 is brought into the switching position in which the pressure fluid, over the control line (not designated) opens the nonreturn valve 27. Under the action of the pump pressure and the weight of ring rail 1 itself, working piston 6 presses the pressure fluid out of the right-hand chamber of working cylinder 5 through short-circuit line 26 now opened for the flow direction from right to left, under increased pressure, as well as under the suction effect of the lefthand side of working piston 6, into the left-hand chamber of working cylinder 5. On the piston movement there occurring there is additionally superimposed the piston movement arising from the pump conveyance, so that the piston speed is considerably increased over the traverse speeds. The ring rail travels back at high speed to its starting position for the commencement of a new winding formation. It has proved that the effect of the weight of the ring rail itself on working piston 6 fully suflices to lower the ring rail 1 at a high speed into the lower starting position. As blocking member in the short-circuit line 26 there can be arranged, if need be, merely a hydraulically operated blocking slide valve.

Obviously many modifications and variations of the invention as hereinbefore set forth may be made without departing from the spirit and scope thereof, and there fore only such limitations should be imposed as are indicated in the appended claims.

We claim i 1. In an improved process for distributing thread with a large crossing angle outside of the winding process proper in the return of the ring or spindle rail of spinning and ring twist machines to its lowered starting position wherein the rail is hydraulically driven upwardly and downwardly and wherein the hydraulic drive means has a range of movement extending axially beyond the winding construction, which improvement comprises: conveying an amount of pressure fluid per unit time into and out of the working cylinder of the hydraulic drive means which is greater than that during the main winding process when it is desired to return said rail to its lowered starting position and wherein it is desired to move said rail from said starting position to the point wherein the traverse movement is to be commenced, and regulating said amount of pressure fluid according to the desired crossing angle and according to the amount of'thread reserve desired on the end of the spindle.

2. An improved hydraulically driven traverse mechanism for moving the ring or spindle rail of spinning and ring twist machines, said hydraulically driven mechanism having a range of movement extending axially beyond the winding construction which comprises: a hydraulic cylinder; a working piston and piston rod movably positioned within said cylinder; a pump; flow lines connecting said pump to each side of said working piston; flow control means operatively associated with said flow lines and said cylinder for controlling the passage of fluid into and out of each side of said cylinder; a switching feeler mounted on the piston rod of said piston; means associated with said switching feeler for actuating the flow of liquid into one or the other of said sides of said cylinder; a ring or spindle rail operatively associated with said piston rod for vertical movement; means for passing an additional amount of pressure fluid per unit time into one or the other of said sides of said cylinder when it is desired to move said rail to its lowered starting position, and means for adjusting said additional amount of pressure fluid.

3. An improved hydraulically driven traverse mechanism as in claim 2 wherein said additional pressure fluid per unit time is supplied by a pressure storing vessel, said vessel being connected to said flow lines by a branch from the pressure line between a control valve for reversing the direction of the pressure fluid acting on alternate sides of the piston and said pressure pump.

4. Apparatus as in claim 2 wherein the pressure pump utilized to pump fluid into said hydraulic cylinder has a variable capacity.

5. Apparatus as in claim 2 wherein a motor driving the pressure pump is infinitely or stepwise variable with respect to its rotation revolution.

6. Apparatus as in claim 2 wherein the two chambers of the working cylinder are connected by means of a short-circuit line in which one or more blocking members are provided, at least one of which is controllable.

References Cited UNITED STATES PATENTS 3,061,236 10/1962 Lang 242-158.4 3,109,606 11/1963 Kubilos 242-458 3,130,930 4/1964 Miller 57-98 OTHER REFERENCES General Motors Corporation, German DAS No. 1,036,- 650, published Aug. 14, 1958.

Neumiinstansche Maschinenbau G.m.b.H., German DAS No. 1,157,118, published Nov. 7, 1963.

Zinser Textilmaschinen G.m.b.H., German DAS No. 1,157,517, published Nov. 14, 1963.

FRANK I. COHEN, Primary Examiner. W. H. SCHROEDER, Assistant Examiner. 

